CN104100525A - Refrigerating circulating device and rotating type compressor thereof - Google Patents
Refrigerating circulating device and rotating type compressor thereof Download PDFInfo
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- CN104100525A CN104100525A CN201410315546.6A CN201410315546A CN104100525A CN 104100525 A CN104100525 A CN 104100525A CN 201410315546 A CN201410315546 A CN 201410315546A CN 104100525 A CN104100525 A CN 104100525A
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Abstract
The invention discloses a refrigerating circulating device and a rotating type compressor of the refrigerating circulating device. The rotating type compressor comprises a shell, a motor and a compression mechanism, wherein the motor is arranged in the shell, the compression mechanism comprises an air cylinder component with two opened ends, a main bearing, an auxiliary bearing, a crankshaft and a piston, the main bearing and the auxiliary bearing are arranged at the two ends of the air cylinder component respectively, and a compression cavity is jointly defined by the main bearing, the auxiliary bearing and the air cylinder component. The crankshaft comprises a main shaft segment, an eccentric shaft segment and an auxiliary shaft segment, wherein the main shaft segment, the eccentric shaft segment and the auxiliary shaft segment are sequentially connected in the axial direction, the main shaft segment is connected with the motor, an eccentric portion is arranged on the eccentric shaft segment, the eccentric portion is arranged in the compression cavity, the eccentric portion is sleeved with the piston, and the piston can roll along the inner wall of the compression cavity. The contact length of the eccentric portion and the piston is L, the diameter of the eccentric portion is Db, and the L/Db meets the formula that L/Db is larger than or equal to 0.39 and smaller than or equal to 0.49. According to the rotating type compressor, frictional losses of the compression mechanism of the rotating type compressor can be reduced, and therefore the rotating type compressor with the high performance can be obtained.
Description
Technical field
The present invention relates to art of refrigeration units, especially relate to a kind of refrigerating circulatory device and rotary compressor thereof.
Background technique
Rotary compressor is provided with motor and compressing mechanism in its seal casinghousing, and the warping force of motor is delivered to compressing mechanism by bent axle, and in compressing mechanism compression refrigerant.The mechanical efficiency that promotes compressing mechanism is one of effective means promoting rotary compressor efficiency, by the physical dimension of each parts in its compressing mechanism is optimized and makes it reach optimum value, thereby promote the mechanical efficiency of compressing mechanism, further reach the object that promotes rotary compressor efficiency.
Yet traditional rotary compressor, when promoting rotary compressor efficiency, only considers to reduce the slip loss of leakage loss and bent axle, thereby do not meet the efficient design requirement of rotary compressor.
Summary of the invention
The present invention is intended at least solve one of technical problem existing in prior art.For this reason, one object of the present invention is to propose a kind of rotary compressor, in the compressing mechanism of described rotary compressor each part dimension in optimal design scope, thereby improved the performance of rotary compressor.
Another object of the present invention is to propose a kind of refrigerating circulatory device with above-mentioned rotary compressor.
Rotary compressor according to first aspect present invention embodiment, comprising: housing, motor, described motor is located in described housing, and compressing mechanism, described compressing mechanism comprises the cylinder assembly of both ends open, main bearing, supplementary bearing, crankshaft and piston, described main bearing and described supplementary bearing are located at respectively the described two ends of described cylinder assembly, described main bearing, described supplementary bearing and described cylinder assembly limit compression chamber jointly, described bent axle comprises vertically connected successively main shaft section, eccentric shaft part and countershaft section, described main shaft section is connected with described motor, on described eccentric shaft part, there is eccentric part, described eccentric part is positioned at described compression chamber, described piston sleeve is located on described eccentric part and can rolls along the inwall of described compression chamber, the contact length of described eccentric part and described piston is L, the diameter of described eccentric part is Db, wherein L/Db meets: 0.39≤L/Db≤0.49.
According to the rotary compressor of the embodiment of the present invention, when L/Db meets 0.39≤L/Db≤0.49, can reduce the frictional loss of the compressing mechanism of rotary compressor, thereby realize, there is high performance rotary compressor.
Preferably, described L/Db=0.44.
Further, described cylinder assembly comprises N cylinder, and described in each, the height of cylinder is H, and described in each, the internal diameter of cylinder is Da, and wherein H/Da meets: 0.41/N≤H/Da≤0.49/N, wherein, described N is more than or equal to 1 integer.
Alternatively, described N=1, described H/Da meets: 0.41≤H/Da≤0.49.
Preferably, described H/Da=0.45.
Or alternatively, described N=2, described H/Da meets: 0.205≤H/Da≤0.245.
Further, the diameter of described countershaft section is Ds, and the offset of described eccentric part is e, and wherein Db-Ds-2e meets: Db-Ds-2e≤0.6mm.
Alternatively, the refrigerant in described rotary compressor is R22, R410A or R32.
According to second aspect present invention embodiment's refrigerating circulatory device, comprise the rotary compressor of the above-mentioned first aspect embodiment according to the present invention.
Additional aspect of the present invention and advantage in the following description part provide, and part will become obviously from the following description, or recognize by practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage accompanying drawing below combination obviously and is easily understood becoming embodiment's description, wherein:
Fig. 1 is according to the longitudinal sectional drawing of the rotary compressor of the embodiment of the present invention;
Fig. 2 is the transverse cross-sectional view of the rotary compressor shown in Fig. 1;
Fig. 3 is the total friction head of the compressing mechanism of the rotary compressor shown in Fig. 1, the slippage loss of slide plate side, the graph of relation of other slippage loss sum and H/Da except slide plate side;
Fig. 4 is the COP (Coefficient of Performance, the coefficient of performance) of the rotary compressor shown in Fig. 1 and the graph of relation of H/Da;
Fig. 5 is the COP of the rotary compressor shown in Fig. 1 and the graph of relation of Db-Ds-2e;
Fig. 6 is the COP of the rotary compressor shown in Fig. 1 and the graph of relation of L/Db.
Reference character:
100: rotary compressor;
1: housing;
2: motor; 21: stator; 22: rotor;
31: cylinder; 311: compression chamber; 3111: air aspiration cavity; 3112: exhaust cavity;
32: main bearing; 33: supplementary bearing;
34: bent axle; 341: main shaft section; 3421: eccentric part; 343: countershaft section;
35: piston; 36: slide plate.
Embodiment
Describe embodiments of the invention below in detail, described embodiment's example is shown in the drawings, and wherein same or similar label represents same or similar element or has the element of identical or similar functions from start to finish.Below by the embodiment who is described with reference to the drawings, be exemplary, only for explaining the present invention, and can not be interpreted as limitation of the present invention.
In description of the invention, it will be appreciated that, term " " center ", " longitudinally ", " laterally ", " length ", " width ", " thickness ", " on ", D score, " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", " outward ", " axially ", " radially ", orientation or the position relationship of indications such as " circumferentially " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, rather than device or the element of indication or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as limitation of the present invention.In description of the invention, except as otherwise noted, the implication of " a plurality of " is two or more.
In description of the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and for example, can be to be fixedly connected with, and can be also to removably connect, or connect integratedly; Can be to be directly connected, also can indirectly be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, can concrete condition understand above-mentioned term concrete meaning in the present invention.
Below with reference to Fig. 1-Fig. 6, describe according to first aspect present invention embodiment's rotary compressor 100, rotary compressor 100 can be vertical compressor.In description below the application, the rotary compressor 100 of take describes as vertical compressor as example.Certainly, those skilled in the art are appreciated that rotary compressor 100 can also be horizontal compressor.
Here, it should be noted that, when this rotary compressor 100 is vertical compressor, the central axis of bent axle 34 is approximately perpendicular to the attachment face of rotary compressor 100; When rotary compressor 100 is horizontal compressor, the attachment face almost parallel of the central axis of bent axle 34 and rotary compressor 100.
As depicted in figs. 1 and 2, the rotary compressor 100 according to first aspect present invention embodiment, comprises housing 1, motor 2 and compressing mechanism.
Motor 2 is located in housing 1, compressing mechanism comprises the cylinder assembly of both ends open, main bearing 32, supplementary bearing 33, bent axle 34 and piston 35, main bearing 32 and supplementary bearing 33 are located at respectively the two ends of cylinder assembly, main bearing 32, supplementary bearing 33 and cylinder assembly limit compression chamber 311 jointly, bent axle 34 comprises vertically connected successively main shaft section 341, eccentric shaft part and countershaft section 343, main shaft section 341 is connected with motor 2, on eccentric shaft part, there is eccentric part 3421, eccentric part 3421 is positioned at compression chamber 311, piston 35 is set on eccentric part 3421 and can rolls along the inwall of compression chamber 311.
See figures.1.and.2, rotary compressor 100 is mainly by housing 1, these three parts of motor 2 and compressing mechanism form, wherein, motor 2 and compressing mechanism are all located in housing 1, and cylinder assembly comprises a cylinder 31, the top of this cylinder 31 and bottom are all opened wide, main bearing 32 and supplementary bearing 33 are located at respectively the two ends up and down of cylinder 31, main bearing 32, supplementary bearing 33 and cylinder 31 limit compression chamber 311, bent axle 34 extends along the vertical direction, and be followed successively by from top to bottom main shaft section 341, eccentric shaft part and countershaft section 343, main bearing 32 is set in main shaft section 341, supplementary bearing 33 is set in countershaft section 343, eccentric part 3421 is positioned on eccentric shaft part, and the central axis disalignment of the central axis of eccentric part 3421 and main shaft section 341 arranges, eccentric part 3421 is positioned at compression chamber 311 to drive sheathed piston 35 thereon in compression chamber 311 rollings, on cylinder 31, be formed with the vane slot radially extending, slide plate 36 is located in vane slot movably, and the periphery wall of the inner of slide plate 36 and piston 35 forms cam mechanism and compression chamber 311 is divided into air aspiration cavity 3111 and exhaust cavity 3112, thereby can compress the refrigerant entering in compression chamber 311.It should be noted that, direction " interior " is the direction towards cylinder 31 centers, and its opposite direction is defined as " outward ", away from the direction at cylinder 31 centers.
Motor 2 comprises stator 21 and rotor 22, rotor 22 closely cooperates with the main shaft section 341 of bent axle 34, and main shaft section 341 support rotor 22, main bearing 32 and supplementary bearing 33 that bent axle 34 can rotate freely compressed mechanism support, motor 2 drives piston 35 eccentric rotaries with slide plate 36 to-and-fro motion by bent axle 34, thereby realizes suction and the compression process of refrigerant.
Alternatively, the refrigerant in rotary compressor 100 is R22, R410A or R32 etc.The type that is appreciated that refrigerant can be according to dissimilar rotary compressor 100 and adaptive change, and the present invention does not do concrete restriction to this.
The ratio L/Db of the contact length L of eccentric part 3421 and piston 35 and the diameter Db of eccentric part 3421 directly has influence on eccentric part 3421 external diameters of bent axle 34 and the oil slick thickness between piston 35 internal diameters, that is to say, the increase of oil slick thickness can improve the frictional loss between eccentric part 3421 external diameters and piston 35 internal diameters.Inventor finds through experimental study: parabolic relation that the ratio of L/Db and the pass of oil slick thickness are tied to form that Open Side Down, as shown in Figure 6, the relation curve of the COP of L/Db and rotary compressor 100 is roughly the parabola that Open Side Down, there is an optimal design scope in the ratio of L/Db and the relation of COP, when L/Db meets 0.39≤L/Db≤0.49, eccentric part 3421 external diameters of bent axle 34 and the oil slick thickness between piston 35 internal diameters reach maximum value, thereby can obtain the rotary compressor 100 of high energy efficiency.Preferably, L/Db=0.44.Be worth to understand the length of the contact segment that " contact length L " refers to the periphery wall of eccentric part 3421 and the inner circle wall of piston 35 in eccentric part 3421 axial.
Here, it should be noted that, when cylinder assembly comprises a plurality of cylinder 31, on bent axle 34, there are a plurality of eccentric parts 3421 that are spaced apart from each other vertically, wherein, Db is the diameter of each eccentric part 3421, contact length L is each eccentric part 3421 and the contact length that is set in the piston 35 on this eccentric part 3421, thereby, each eccentric part 3421 all should meet with the corresponding contact length L of piston 35 and the ratio L/Db of the diameter of this eccentric part 3421: 0.39≤L/Db≤0.49, to improve the mechanical efficiency of compressing mechanism, and then the efficiency of lifting rotary compressor 100.
According to the rotary compressor 100 of the embodiment of the present invention, when L/Db meets 0.39≤L/Db≤0.49, can reduce the frictional loss of the compressing mechanism of rotary compressor 100, thereby realize, there is high performance rotary compressor 100.
According to one embodiment of present invention, cylinder assembly comprises N cylinder 31, and the height of each cylinder 31 is H, and the internal diameter of each cylinder 31 is Da, and wherein H/Da meets:
0.41/N≤H/Da≤0.49/N
Wherein, N is more than or equal to 1 integer.
The discharge volume V of rotary compressor 100 can be tried to achieve by formula below:
V≈πe(Da-e)H
Wherein, the internal diameter of cylinder 31 is Da, and the height of cylinder 31 is H, and the offset of eccentric part 3421 is e.
From formula above, can find out, when eliminating volume V one timing of compressor, can realize by changing cylinder 31 inside diameter D a, cylinder 31 height H and eccentric amount e.
Discharge volume V one timing when rotary compressor 100, along with reducing of cylinder 31 height H, can cause the increase of eccentric amount e and slide plate 36 movement velocitys, thereby cause the stressed deterioration of slide plate 36 sides, oil slick thickness reduces, surface friction drag increases, and finally causes slide plate 36 side frictional losss to increase.With reference to Fig. 3, S1 represents the relation curve between slide plate 36 Slideslip losses and the ratio of H/Da, S2 represents the relation curve between other slippage loss and the ratio of H/Da except slide plate 36 sides, S3 represents the relation curve between the total slippage loss of compressing mechanism and the ratio of H/Da, wherein, the relation curve of the ratio of H/Da and slide plate 36 slippage loss is around roughly the straight line of a monotone decreasing, when rotary compressor is discharged volume one regularly, along with reducing of the H/Da of rotary compressor 100, slide plate 36 slip loss around increases gradually, in other words, increase along with the H/Da of rotary compressor 100, slide plate 36 slippage loss around reduces gradually.
And, along with reducing of cylinder 31 height H, the increase of eccentric amount e, can cause reducing of piston 35 height and external diameter, the lifting surface area of piston 35 outer surfaces is reduced, thereby improve the stressed of bent axle 34 eccentric parts 3421, main shaft section 341 and countershaft section 343, the oil slick thickness between eccentric shaft and piston 35, main shaft section 341 and main bearing 32 and countershaft section 343 and supplementary bearing 33 is increased, frictional loss reduces.Yet, as can be seen from Figure 3, due to reducing along with H/Da, the gathering way of slide plate 36 frictional loss is around greater than the speed that reduces of frictional loss between eccentric shaft and piston 35, main shaft section 341 and main bearing 32 and countershaft section 343 and supplementary bearing 33, finally cause the total friction head of compressing mechanism to the future development increasing, now the relation curve of the ratio of H/Da and the total friction head of compressing mechanism is roughly the straight line of a monotone decreasing equally, as shown in Figure 3.
Along with reducing of H/Da, the amount of leakage of rotary compressor 100 reduces gradually, that is to say, the leakage loss of rotary compressor 100 can reduce gradually, but time, as can be known from Fig. 3, along with reducing of H/Da, total frictional loss meeting between each moving element of compressing mechanism increases gradually, therefore, obtain high performance rotary compressor 100, the relation of its H/Da ratio and COP must not be monotone increasing or the dull relation reducing, inventor finds through experimental study: between the H/Da ratio of rotary compressor 100 and COP, meet the relation curve shown in Fig. 4, as can be seen from Figure 4, in order to promote the performance of rotary compressor 100, in order to obtain a higher COP value, H/Da has an optimized scope, i.e. 0.41≤H/Da≤0.49, wherein H/Da is preferably 0.45.Thus, when the discharge volume V of rotary compressor is certain and during 0.41≤H/Da≤0.49, the COP of rotary compressor can remain on optimal design scope.
Thus, by optimizing the ratio of H/Da, when reducing leakage loss and frictional loss, improved the mechanical efficiency of compressing mechanism, thereby further promoted the efficiency of rotary compressor 100.
Here, it should be noted that, what talk about above is the single cylinder compressor with a cylinder 31 shown in Fig. 1, i.e. N=1, and the height of this cylinder 31 is H, and internal diameter is Da, and wherein H/Da meets: 0.41≤H/Da≤0.49.For the multicylinder compressor with a plurality of cylinders 31, N is greater than 1 integer, wherein the height of each cylinder 31 is H, corresponding internal diameter is Da, wherein each in a plurality of cylinders 31 all meets: 0.41/N≤H/Da≤0.49/N, for example, when N=2, the ratio H/Da of the height of each cylinder 31 and internal diameter meets: 0.205≤H/Da≤0.245.
For discharging volume V, the high H of cylinder, the diameter Ds of countershaft section 343 and the certain rotary compressor 100 of the eccentric amount e of eccentric part 3421, along with reducing of eccentric part 3421 diameter Db, corresponding the reducing of friction area between bent axle 34 eccentric parts 3421 and piston 35 internal diameters, thereby frictional loss reduces, the final lifting that obtains COP, as can be seen from Figure 5,, along with reducing of Db-Ds-2e in rotary compressor, COP becomes increase trend.Yet due to the restriction of rotary compressor 100 assembly relations, Db>Ds+2e is known, it is very little that the eccentric footpath Db of bent axle 34 can not do, so the present invention has provided the optimum design scope of Db:
Db-Ds-2e≤0.6mm
Thus, can effectively guarantee the performance of rotary compressor 100.
The rotary compressor 100 of a plurality of embodiments according to the present invention is described below with reference to Fig. 1 and Fig. 2.
Embodiment one,
As depicted in figs. 1 and 2, in the present embodiment, rotary compressor 100 comprises seal casinghousing 1 and is accommodated in motor 2 and the compressing mechanism in housing 1, compressing mechanism comprises a cylinder 31, bent axle 34, main bearing 32, supplementary bearing 33, piston 35 and slide plate 36, the warping force of motor is delivered to above-mentioned compressor structure by bent axle 34, and in compressing mechanism compressed refrigerant.When forming the internal diameter of the cylinder 31 of above-mentioned compressor structure, be that Da, cylinder 31 are highly that eccentric part 3421 diameters of H, bent axle 34 are that the offset of Db, eccentric part 3421 is that contact length between e, eccentric part 3421 and piston 35 is that the diameter of the countershaft section 343 of L, bent axle 34 is while being Ds, 0.41≤H/Da≤0.49, and meet relation Db-Ds-2e≤0.6, and 0.39≤L/Db≤0.49.
According to the rotary compressor 100 of the present embodiment, can make each parts in compressing mechanism reach optimal design scope, thereby when reducing rotary compressor 100 leakage loss, reduce the frictional loss between each moving element, finally obtain high performance rotary compressor 100.
Embodiment two,
The structure of the rotary compressor 100 of the present embodiment and embodiment one structure are roughly the same, and wherein identical parts adopt identical reference character, and difference is only: cylinder assembly comprises two cylinders 31.
In the present embodiment, between two cylinders 31, can separate by dividing plate, on bent axle 34, there are two eccentric parts 3421 that are axially spaced apart from each other along it, each eccentric part 3421 is outer is all arranged with a piston 35, when bent axle 34 rotates, can drive two pistons 35 at the interior compression refrigerant of corresponding compression chamber 311.Each in two cylinders 31 that form above-mentioned compressor structure all meets: the internal diameter of cylinder 31 be Da, cylinder 31 be highly H, eccentric part 3421 diameters be the offset of Db, eccentric part 3421 be e, eccentric part 3421 with corresponding piston 35 between contact length be L, and when the diameter of countershaft section 343 is Ds, have: 0.205≤H/Da≤0.245, Db-Ds-2e≤0.6, and 0.39≤L/Db≤0.49.
According to the rotary compressor 100 of the present embodiment, it is duplex cylinder compressor, in its compressing mechanism, by upper cylinder and lower cylinder, formed, therefore with in embodiment one, discharge the single cylinder compressor that volume V is identical and compare, at Da, Ds, what when e is constant, the single cylinder 31 of the present embodiment highly can be done is less, what guarantee that in the situation of ceteris paribus, H/Da ratio can be done is less, thereby further reduce leakage losses and the frictional loss of compressing mechanism, therefore in the rotary compressor 100 of the present embodiment 2, meet 0.205≤H/Da≤0.245, Db-Ds-2e≤0.6, and 0.39≤L/Db≤0.49 o'clock, can realize and obtain the more rotary compressor 100 of high energy efficiency.
Thus, according to the rotary compressor 100 of the embodiment of the present invention, when realizing leakage loss and slip loss reduction, further reduce the frictional loss of rotary compressor 100 compressing mechanisms, final realization has high performance rotary compressor 100, and adopts this rotary compressor 100 to obtain the object of the refrigerating circulatory device of refrigeration cycle efficiengy-increasing.
According to second aspect present invention embodiment's refrigerating circulatory device (scheming not shown), comprise the rotary compressor 100 of the above-mentioned first aspect embodiment according to the present invention.
In the description of this specification, the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present invention or example in conjunction with specific features, structure, material or the feature of this embodiment or example description.In this manual, the schematic statement of above-mentioned term is not necessarily referred to identical embodiment or example.And the specific features of description, structure, material or feature can be with suitable mode combinations in any one or more embodiments or example.
Although illustrated and described embodiments of the invention, those having ordinary skill in the art will appreciate that: in the situation that not departing from principle of the present invention and aim, can carry out multiple variation, modification, replacement and modification to these embodiments, scope of the present invention is limited by claim and equivalent thereof.
Claims (9)
1. a rotary compressor, is characterized in that, comprising:
Housing;
Motor, described motor is located in described housing; And
Compressing mechanism, described compressing mechanism comprises the cylinder assembly of both ends open, main bearing, supplementary bearing, crankshaft and piston, described main bearing and described supplementary bearing are located at respectively the described two ends of described cylinder assembly, described main bearing, described supplementary bearing and described cylinder assembly limit compression chamber jointly, described bent axle comprises vertically connected successively main shaft section, eccentric shaft part and countershaft section, described main shaft section is connected with described motor, on described eccentric shaft part, there is eccentric part, described eccentric part is positioned at described compression chamber, described piston sleeve is located on described eccentric part and can rolls along the inwall of described compression chamber, the contact length of described eccentric part and described piston is L, the diameter of described eccentric part is Db, wherein L/Db meets:
0.39≤L/Db≤0.49。
2. rotary compressor according to claim 1, is characterized in that, described L/Db=0.44.
3. rotary compressor according to claim 1, is characterized in that, described cylinder assembly comprises N cylinder, and described in each, the height of cylinder is H, and described in each, the internal diameter of cylinder is Da, and wherein H/Da meets:
0.41/N≤H/Da≤0.49/N
Wherein, described N is more than or equal to 1 integer.
4. rotary compressor according to claim 3, is characterized in that, described N=1, and described H/Da meets:
0.41≤H/Da≤0.49。
5. rotary compressor according to claim 4, is characterized in that, described H/Da=0.45.
6. rotary compressor according to claim 3, is characterized in that, described N=2, and described H/Da meets:
0.205≤H/Da≤0.245。
7. according to the rotary compressor described in any one in claim 1-6, it is characterized in that, the diameter of described countershaft section is Ds, and the offset of described eccentric part is e, and wherein Db-Ds-2e meets:
Db-Ds-2e≤0.6mm。
8. rotary compressor according to claim 1, is characterized in that, the refrigerant in described rotary compressor is R22, R410A or R32.
9. a refrigerating circulatory device, is characterized in that, comprises according to the rotary compressor described in any one in claim 1-8.
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| CN201410315546.6A CN104100525A (en) | 2014-07-02 | 2014-07-02 | Refrigerating circulating device and rotating type compressor thereof |
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| CN201410315546.6A CN104100525A (en) | 2014-07-02 | 2014-07-02 | Refrigerating circulating device and rotating type compressor thereof |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632621A (en) * | 2015-02-04 | 2015-05-20 | 广东美芝制冷设备有限公司 | Refrigerating system and rotating compressor of refrigerating system |
| CN105201845A (en) * | 2015-10-22 | 2015-12-30 | 广东美芝制冷设备有限公司 | Rotary compressor |
| WO2016123765A1 (en) * | 2015-02-04 | 2016-08-11 | 广东美芝制冷设备有限公司 | Refrigeration system and rotating compressor thereof |
| CN106385117A (en) * | 2016-11-29 | 2017-02-08 | 安徽美芝制冷设备有限公司 | Motor used for compressor and compressor |
| CN107446671A (en) * | 2017-07-28 | 2017-12-08 | 广东美芝制冷设备有限公司 | Refrigeration plant and its rotary compressor and heat conduction lubricating oil |
| WO2018076480A1 (en) * | 2016-10-26 | 2018-05-03 | 上海海立电器有限公司 | Crankshaft and rotary compressor |
| CN113323878A (en) * | 2021-06-22 | 2021-08-31 | 广东美芝制冷设备有限公司 | Compression and exhaust mechanism, compressor and refrigeration equipment |
| CN114109821A (en) * | 2021-11-09 | 2022-03-01 | 广东美芝精密制造有限公司 | Compression mechanism, compressor and refrigeration plant |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101684792A (en) * | 2008-09-22 | 2010-03-31 | 东芝开利株式会社 | Rotary compressor and freezing cycle device using the same |
| US20100147020A1 (en) * | 2007-08-28 | 2010-06-17 | Toshiba Carrier Corporation | Rotary compressor and refrigeration cycle equipment |
| CN102889209A (en) * | 2012-09-27 | 2013-01-23 | 广东美芝精密制造有限公司 | Compression pump body, rotary compressor and refrigerating circulating device |
| CN203516107U (en) * | 2012-10-01 | 2014-04-02 | 三菱电机株式会社 | Rotary compressor |
| CN103727038A (en) * | 2013-12-26 | 2014-04-16 | 广东美芝精密制造有限公司 | Rotary compressor, air cylinder and refrigerating system thereof, and air conditioner |
| CN203962387U (en) * | 2014-07-02 | 2014-11-26 | 广东美芝制冷设备有限公司 | Refrigerating circulatory device and rotary compressor thereof |
-
2014
- 2014-07-02 CN CN201410315546.6A patent/CN104100525A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20100147020A1 (en) * | 2007-08-28 | 2010-06-17 | Toshiba Carrier Corporation | Rotary compressor and refrigeration cycle equipment |
| CN101684792A (en) * | 2008-09-22 | 2010-03-31 | 东芝开利株式会社 | Rotary compressor and freezing cycle device using the same |
| CN102889209A (en) * | 2012-09-27 | 2013-01-23 | 广东美芝精密制造有限公司 | Compression pump body, rotary compressor and refrigerating circulating device |
| CN203516107U (en) * | 2012-10-01 | 2014-04-02 | 三菱电机株式会社 | Rotary compressor |
| CN103727038A (en) * | 2013-12-26 | 2014-04-16 | 广东美芝精密制造有限公司 | Rotary compressor, air cylinder and refrigerating system thereof, and air conditioner |
| CN203962387U (en) * | 2014-07-02 | 2014-11-26 | 广东美芝制冷设备有限公司 | Refrigerating circulatory device and rotary compressor thereof |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632621A (en) * | 2015-02-04 | 2015-05-20 | 广东美芝制冷设备有限公司 | Refrigerating system and rotating compressor of refrigerating system |
| WO2016123765A1 (en) * | 2015-02-04 | 2016-08-11 | 广东美芝制冷设备有限公司 | Refrigeration system and rotating compressor thereof |
| CN104632621B (en) * | 2015-02-04 | 2017-03-29 | 广东美芝制冷设备有限公司 | Refrigeration system and its rotary compressor |
| CN105201845A (en) * | 2015-10-22 | 2015-12-30 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN105201845B (en) * | 2015-10-22 | 2017-11-07 | 广东美芝制冷设备有限公司 | Rotary compressor |
| WO2018076480A1 (en) * | 2016-10-26 | 2018-05-03 | 上海海立电器有限公司 | Crankshaft and rotary compressor |
| EP3534006A4 (en) * | 2016-10-26 | 2019-09-25 | Shanghai Highly Electrical Appliances Co., Ltd. | Crankshaft and rotary compressor |
| CN106385117A (en) * | 2016-11-29 | 2017-02-08 | 安徽美芝制冷设备有限公司 | Motor used for compressor and compressor |
| CN107446671A (en) * | 2017-07-28 | 2017-12-08 | 广东美芝制冷设备有限公司 | Refrigeration plant and its rotary compressor and heat conduction lubricating oil |
| CN113323878A (en) * | 2021-06-22 | 2021-08-31 | 广东美芝制冷设备有限公司 | Compression and exhaust mechanism, compressor and refrigeration equipment |
| CN114109821A (en) * | 2021-11-09 | 2022-03-01 | 广东美芝精密制造有限公司 | Compression mechanism, compressor and refrigeration plant |
| CN114109821B (en) * | 2021-11-09 | 2023-10-24 | 广东美芝精密制造有限公司 | Compression mechanism, compressor and refrigeration equipment |
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